Rotary, multiple turbine hydraulic coupling



m, S., 3 1 KY v/ 2 T ma M nl m NW P 7 5. 2 s. ww s, G NS u2 y w n w E .C I L Dwi mu 9. YM EI SmURP W.T .E FH mm I m Wm :1 m mn O. Rt C 3 O Lb .w 1 u f F 0 l l m .n .mv e. i F m Feb. 10, 1953 F. w. sl-:YBOLD ROTARY, MULTIPLE TURBINE HYDRAULIC COUPLING 2 SHEETS-*SHEET 2 Original Filed Oct. 11, 1949 AIYUEIVEYS.-

Patented Feb. 10, 1953 TENT OFFICE ROTARY, l'i/IULTIPLE TURBINE HYDRAULIC COUPLING Frederick W. Seybold, Westfield, j.

originaiappneauen oeuvrerV 11, 1949, stringhe. reorganowratent No. 2,548,272; dated-Apre 6 Claims. 1

This invention relates to automatic variable speed transmissions, particularly of the type adapted for transmitting power from an engine to the driving wheels of yan automotive vehicle. More particularly still, this invention is concerned with that type of transmission which utilizes a uid coupling and to an improved and novel design of fluidV coupling therefor. y

Automatic transmissions of the type referred to are well known in the art and may generally be divided into two groups. The iirst group hasl a fluid cupling and gear sets, such as planetary gear sets, which are equipped with brakes and clutches `for providing the various driving ratios between the input and output shafts. Due to the fact that brakes and clutches are employed for changing from one driving ratio to another, noticeable steps are obtained as the changes in speed ratio occur due to the operation of said clutches and brakes.

The second group of transmissions employs torque converters and gea-r sets, but, due' to the lower efliciency of the converters,- additional gear sets are generally required for reverse operation and for the higher torque requirements. The inemciency of this type of unit causes the generation of a great dealof heat and this,- in turn; requires cooling facilities for the hydraulic fluid which represents an expense and a complication.

En connection with both types of transmissions referred to, fairly elaborate controls are required and this, of course, is expensive and also a source of trouble during the life of the transmission.

A particular object of this invention is the' provision of a transmission of the type referred to having a new and novel design of uid coupling which substantially eliminates the need for clutches and brakes for effecting changes in the driving ratio of the transmission.

-another object is the provision of a novel type of fluid coupling especially adapted for use with an automatic transmission which substantially eliminates noticeable steps when the transmission changes from one driving ratio to another.

It is also an object of this inventin to provide a nuid coupling of general utility having a piu rality of output members which become succes sively eectiv'e during operation of the transmission for providing driving ratio changes.

These and other objects and advantages wiil become more apparent upon reference to the following description taken in connection with the accompanying drawings in which:

g Figure 1 is a vertical longitudinal section.

'10, :1951. 'Divided and this application Mar 12, 1950, Serial No. 161,682

2 through a uid coupling and transmission according to this invention.

Figure 2 is a perspective view showingthe yieldable shell forming a part of the fluid coupling of the transmission.

Figure 3 is a fragmentary -view indicated by line 3--3 on Figure lland showing the arrangement of the -iieiiible' shell in the' impeller of the coupling; and

Figure 4 is a fragmentary view of a part of the fluid coupling showing the yieldable shell after it has yielded to its outermost position.

The combination of the novel fluid coupling and automatic transmission according to my invention comprises' what may be referred to as eight assemblies or units; an assembly or unit comprising connected parts capable of rotating at a different speed from the other assemblies of the transmission. The units may, o'f course, be held stationary at certain instances.

The detailed construction of the transmission and its operation are fully set forth in my copending application, Serial No. 129,649, led Octoberill, 1949, now Patent No. 2,543,272fissued April 10, 1951, andof which the instant application is a division, but a brief resume of the con struction will be given here in order to' make this disclosure complete ineveryrespect.

Driving assembly' The driving assembly comprises the drive shaft it to the flanged end of which is secured the engine starter gear it and the long multiplesplined shaft l2 by thebolts I3., To said multiple splines is secured the torus shaped ixnpeller 'is which is provided with radial venes or partitohs l5.

A somewhat smallerimpeller iiiy (see Figure 2) is provided with radial slots4 into which the vanes i5 project. This impeller is made of spring steel of suit-able thickness and strength so that it' will fieri' or yield to the centrifugal force exerted bythe circulating oil `of the fluid coupling. rThis impellente is fastenedto the impeller l5 by' the bolts iS.

An internal gear ifi provided with a long n'lultiple-splined hub i8 is alsovsecured to the long shaft i2. A ball bearing i9 and one element of an overrunning clutch 20de-carried on the: left hand eid of the' long hub I. At the eX- treme right hai-id end one element of an overrunning clutch! 2 lv is seed.

The drive shaft l0 and-the' shaft i2` are provided with dil passages 2N2, 23- and 2H respectively. Th ri-lhand enelv of' the-shaft i2'v is 3 recessed to receive an oil seal and a ball bearing 2G.

Prim-ary floating assembly The primary floating assembly consists of the multiple section casing 2l. The left hand section 28 essentially conforms to the shape of the impeller i4 and is supported on the ball bearing 29 and contains the oil seal 30, both of which operate on the enlarged section 3l of the shaft l2.

The next section 32 consists of the radial vanes S3 and 34, also the torus-shaped shell 35, forming a hydraulic runner which cooperates with the impeller elements ld, I5 and I6.

The third section 36'is shaped to contain the third element of this hydraulic coupling and is supported on the ball bearing 37. The three sections 28, 32 and 36 are bolted together by the screws 38. An oil seal S9 serves to conne the fluid in the coupling and is tted into the casing 3S.

The fourth section itil is a long hanged shell which is secured to section 3E by the bolts alla. The last section 4i is provided with an internal gear |52, a needle bearing 43 and oil seals 44 and it is secured to section by the screws 45.

` Secondary floating assembly The secondary floating assembly comprises three sections, the first section being the third element of the hydraulic coupling, i. e. the runner $6 to which the radial varies 4l are attached. The hub 48 of this runner is journalled in the inner race of the ball bearing 3l. The right hand end of hub 48 has multiple splines 49 which coact with the internal spline teeth 50 of the shell 5l.

The second section comprises the planet pinion carrier 52 which is secured to the shell 5l by screws not shown. Two or more planet pinions 53 are free to turn on needle bearings 5d on the studs 55 secured in the carrier 52. A ball bearing 56 supports the carrier 52. The other elements of the overrunning clutch 2B are conned in the hub of the runner 46.

The third section comprises the internal gear 5l with one element of an overrunning clutch 51a. This internal gear is fastened to member 52 by screws not shown.

Reaction assembly The reaction assembly consists of the duplex sun gear 58 Which has a hub extending to the right, on the external surface of which are formed right hand multiple helical threads 59, and these are engaged by similar multiple helical threads formed within the bore of the multiple teeth brake 60. The left hand end of member 6D is provided with a stop ring 6| which limits the movement of brake 6B to the right for a purpose to be described later. The outer member of an overrunning clutch 62 is confined in the left hand end'of the duplex sun gear 58. A needle bearing 63 is located about midway between the teeth of duplex sun gear '53.

Reverse assembly The reverse assembly comprises a two-piece planeta-ry pinion carrier 64 and 65. The left hand section 65 has a hub 66, the outside of which carries one element of the overrunning clutch 51a and on the inside is mounted the outer race of the needle bearing 63. Theright hand section 64 also has a hub 61, the outside of which carries the inner race of needle bearing 43, While the 4 bore of the hub is provided with internal brake teeth SS. Planet pinions 63 are journalled on needle bearing lil, the latter being carried on pins 'H which are secured in the carriers 66 and $5. rlhe planet pinions 69 mesh with the internal gears 2 and 58a of the duplex sun gears 58.

"High gear assembly The high gear assembly consists of the sun gear l2 which meshes with the planet pinions 53. The bore of gear 'l2 is provided with needle bearings 'i3 and 14. The inner race of ball bearing 5S is also mounted on the long hub of gear l2, as well as the inner member of an overrunning clutch 15, and whose outer member is fitted into the bore of an externally toothed pinion l5, the teeth of which serve to drive the multiple clutch plates l1.

Driven assembly The driven assembly comprises the driven shaft 78, the left hand end of which is journalled in the ball bearing 2S and co-acts with the oil seal 25. The inside member of the over-running clutch 2l is also supported on the driven shaft 'i8 as Well as the needle bearings 'i3 and 'le of the sun gear l2. Integral with the shaft 13 is the planet pinion carrier 79.

Planet pinions are journalled on needle bearings 8|, the latter being carried by the headed pins 32 which are secured in the planet pinion carrier 79. Planet pinions 8) mesh with the internal gears tl and 58h of the duplex sun gears 58.

A longitudinal oil passage 83 is provided in the shaft 18 which aligns with the oil passage 2li of the driving assembly. Radial oil passages 84 lead from passage 83 to the small cylinders 85 in the carrier body 79. Small pistons 86 are slidably tted in the cylinders and these pistons respond to oil pressure.

An internal gear 81 is fastened by the screws x28 to the carrier 18, whose internal teeth drive the multiple clutch plates 59, which alternate with the clutch plates 'Il of the high gear assembly. Needle bearings 99 journal the duplex sun gear 58 on the Shaft 73.

The inner member of overrunning clutch 62 is integral with driven shaft i8 and this clutch prevents the latter from turning in the reverse direction at a speed greater than that of the duplex sun gear 58, or if this sun gear is locked, the driven shaft i8 is prevented from turning in reverse and this feature is usually referred to as no-roll-back.

Control assembly The control assembly comprises the slidable brake member 9i, the position of which relative to the brake 66 and internal brake 68 determines the various speed ratios which will be described later. Member 5i is provided With external spline teeth S2 which are slidably mounted in the internal spline teeth 53 of the stationary transmission casing Se. The member el extends to the left intov the section i of the primary iioating assembly and thereby provides a cylindrical surface for the oil seals (i4 and at its extreme left it is provided with external brake teeth which may be engaged with the internal brake 68 when member 9| is moved to the right by means of well-known shifting mechanisms attached to and operated from the steering Wheel column and terminating in the groove 9S of the member 9 I.

Member 9| is also provided with a bore into previously mentioned the pistons 36 are 1actuated by hydraulicl vfoil pressure to lc'ornzlition the multiple friction disc clutch plates 11 fand 'B9 for transmitting power 'and kupon ?relea'se :of this foi-l pressure the clutch iplate's will .separate and fconsequently transmit .no p'o'wer.

The source of `this .hydraulic pressmte tis usuallyalpump v(not:'shown) whose Ihigh :pressure -iluid --is conducted byspipes to a threadedfitting @93 Kon bearing 99 in `v/hich :an :annular groove fwn fis provided fwhereby the *oil maygainentrance unto' the ports 22 of the drive shaft lU.

Lllssociated .with r.the control llever aand. actuated thereby is'ava'lv'e 2(not1shovvnf) 'Which-Lcontrlsthe flow Iof pressure Acoil lto ithe fcylinders 85 torpermits drainage therefrom.

Operation For `neutral or idling operation isliding :brake finem'ber El! ispo'siteelfih-itsnteriediatepsiftion -a's loy a vsuitable control lever fo'n the I 'steering colu'r'n'n. 'In this position te'e'th "91 Fand @brake teeth 'B -will not engage, land fthe-ifi" `iriilessure iis 'exhausted from cyliider 85. similari-y, *the brake ltee't-h 88 landr are-'prevented from Yengagement. Under these "ciondtitns, the driven fshat 18 will vbe at Vrestlandit'he idplexsun gear italie.

v'-For-vvard koper-ation is v ebt/ined by #shifting the s'lidablebralre-member leftvvardly f lits Figure 'l position so that brake L"teethfl @will lee Within reach of fthefhr-ke t-teetlfi'ill tvPressure fluid is l' also condu'ctedlto cylinder-s forlocking -clutch plates'll-y andi-8B together.

Duplexlsungear i583 'lnow `stationary u:and-the id-'rivelis from themp'eller 'of-'the fluidcoup'lin'g 'to "the runner '3.53, 3623, 35 and its vinternal f'gear 542 "through fthe reverse Yafss'e'x'nbly to -tl-ie `output shaft.

car fa-t vthis time -is moving Vin its 'lowest 'gear ratio v 'With 'the "hpeller' df 'the 'uid 'couf-pling'revlvingat relatively low k'speed andthe its speed and commencing'*totransmt,theltorduel thereto. As this 'action'c'ontinues runnerfin- Lcreases 'its speed until fit 'takes )over "the '.drive vithrough'jgear train" 5MM, *581). YI'he duplexsun "gear continues 'to "remain'stationaryandlthe overrunning clutch 51 'permits the 'Zscondary "iloating "assembly to v-overrun the reverse "assembly.

The speed ratio of the transmission has now been substantially changed but it Will be observed that this has occurred without any noticeable shock or jar. `Wth :a further/increase .in 'the speed of limpeller 156,12. iur-'ther'deflection ptits `cur-ved sections will Foccur fand Ith'ekispeed 'fof 'the run-ner 46 lwill 'fbe :correspondingly lincreased and this speed iincreas'e will `tbe transmitted :to :sun gear-Fi 2.

A still further increase in itl/ie speed fo'i the sun gear fl'zwill bring-:about a :direct drive from `sun ygear through .overrunning lxlutch 15 'and clutch plates 11:1;a'nd'39 todrivenshaft H8, A'thereby placing theltransniissionin its shi'ghest tdrivingratio.

When quick acceleration is desire'duidlpressure 'may 'be :exhausted .troniccylinders 8` 5 thereby releasing clutch plates 1.1`fand'89. flh'is may be accomplished .manually'or 'Iautomati'callylas by fa valve Fresponsive Lto acceleratcr- :setting for to :a combination Yof the accelerator setting .and ithe speed of the vehicle.

Releasing of the clutch plates will increase Sthe driving vratio through the transmission, .and should yconditions tbe such :that fthe Sspeed :of runner '46 drops Itol about` '7.0 percentof itheispeed of Vrunner '533, T34, 35, :the 'power will again loe transmitted 'through the primary :floating nssembly until such 'itime fas runner d5 :can commenceldriving.

For reverse operation, member '91 is :shifted yto its extreme right-hand .position prin'g'ing brake `teeth :into engagementfwithrbraketeeth 68 "thus arresting v:the .rotation :of lthie'ireverse assembly.

The Tdrive `is now I:fromIimpel'ler .jl, `|55, it .to the primary runner 33,1311, .3'5 and *through Jinternaligear F42 to duplex sun 'gear :58, :the said sun gear rotating :inra directioncppcsite tolthat which 'obtains during .forward 'operation fof the vehicle.

Duplex Ysun ,gear 58 I willndrveiinternalsgear 5l vwhichzwill fcause the ;secondaryJoating :assembly `to rotate 'and transmit. power :to-.outputrshaft 118.

.From 'the foregoing it will @be `evident that I yhave devised .an Aautoma-tic 'transmission andra `novel fluid coupling :therefor such .that a Lplu- `rality of speed irratios in vvtheforward direction -can ihe obtained entirely .without the use -of clutches iand .brakes and comp-lex control Atarvrangements therefor. 'A :,single, asixnply iconstructed, nadjustable :brakingffelement yis ieiected for selectively V:placing the transmission yin zforward, ineutral, I:or Lreverse operation. No sliding bands :or `other devices, y:other than ithezpverrunning clutches referred to :and :thai-:multiple dscclutcnare required.

Referring :to theflud cnupling, :the .gyielda'ble shell V.IS Athereof iis zsubjectto :certainfmodicaltions inorder towadapt' itztofdierent conditions of 1 operation andzusages Forxampla .as illusztrated s and describedzthe :entire `,flexibley shell fis adapted foryielding ealtthe V:saine tirnfe. #It will begevident, however, that'underzcertan conditions it may?bedesnablethat-various; partslof the-,shell yield fa't :different speeds :This :may :be accom- 'idividualrngers or blades :of fthe fflexible:shellso they :yield yatwa;I different-,e speed :from .fthe not-hers thereof. y,This :could bexutilized fincertain lin .stances to make the .transition/,ofthe .transmission ifrom one -speedfratio Kto ryanotherfeven `more gradual` than vis how'gobtained.

The yieldableshellghas:beenzillustrated as; yield# wable :by ithe v.centri'iugal:` forcezpf fthe;oi1 acting thereon, but it will be evident that the individual parts of the shell, or certain selected ones thereof, could be Weighted, or otherwise modified so that a predetermined force would be developed thereon for causing the shell to yield due to the rotational speed of the impeller. In this case the shell would be yieldable under the joint influence of the rotational speed of the impeller and the centrifugal force of the oil acting thereon. In general, there will be a fixed relationship between these factors, but in certain types of couplings as, for example, the type in which the oil level is selectively varied, it might be desirable to provide an actuating influence on the yieldable shell apart from the influence of the circulating oil thereon.

It will be understood that this invention is susceptible to modication in order to adapt it to different usages and conditions and, accordingly, it is desired to comprehend such modiications within this invention as may fall within the scope of the appended claims.

I claim:

1. In a iiuid coupling; an impeller having radial partitions, a plurality of concentric runners rotatable relative to each other and to said impeller and each having a semi-toroidal shell with partitions, and curved means on the impeller extending between the partitions thereof and forming a shell smaller than the impeller with its outer peripheral edge normally located in axial alignment with the outer edge of the shell of the inner runner and closely adjacent thereto so the impeller is normally effectively coupled with only the inner of the runners, said curved means being secured to the impeller adjacent its hub and having its outer peripheral edge free for movement whereby a predetermined radial thrust on said means will cause it to yield outwardly and couple the impeller with others oi said runners.

2. In a iluid coupling having a casing, an impeller in the casing having radial partitions, a pair of concentric runners in the casing rotatable relative to each other and to said impeller, each runner having a semi-toroidal shell and partitions, a resilient inner shell member secured to said impeller adjacent the hub thereof and having curved lingers extending between the partitions, said shell member being of substantially1 the same shape as said impeller but smaller and the outer edges of said fingers being normally axially aligned with the outer edge of the shell of the inner of said runners whereby the impeller is normally coupled with only the inner one of the runners, said shell member being yieldable in response to a predetermined outward thrust on the :lingers thereof to effect coupling of the impeller with the outer one of said runners.

3. In a fluid coupling having a casing, an impeller in the casing having radial partitions, a pair of concentric runners in the casing also having partitions rotatable relative to each other and to said impeller, and a resilient inner shell member secured to said impeller adjacent the hub thereof and having curved ngers extending between the partitions, said shell member being of substantially the same shape as said impeller but smaller whereby the impeller is normally coupled with only the inner one of the runners, said shell member being yieldable in response to a predetermined outward thrust on the lingers thereof to eiect coupling of the impeller with the outer one of said runners, said casing being connected to one of said runners and an output member rotatable in the casing connected to the other runner.

4. In a fluid coupling; a casing dening an annular cavity, an impeller rotatable in the casing and comprising radial partitions, a pair of concentric runners in the casing also having partitions, the inner thereof having means extending from its outer edge and connected to said casing and the other comprising an output part extending axially through the casing at one side, and a yieldable shell in the impeller connected thereto adjacent the hub, said shell comprising curved fingers extending between the partitions and terminating in a, circular path adjacent the outer edge of the said inner runner whereby the impeller is normally coupled with only the inner runner but whereby, also, the ngers will yield outwardly at a predetermined speed of said impeller to bring about coupling of the impeller With the outer runner.

5 In a fluid coupling; a casing defining an annular cavity, an impeller rotatable in the casing and comprising radial partitions, a pair of concentric runners in the casing also having partitions, the inner thereof having means extending from its outer edge and connected to said casing and the other comprising an output part extending axially through the casing at one side, and a yieldable shell in the impeller connected thereto adjacent the hub, said shell comprisingr curved fingers extending between the partitions and terminating in a circular path adjacent the outer edge of the said inner runner whereby the impeller is normally coupled with only the inner runner but whereby, also, the fingers will yield outwardly at a predetermied speed of said impeller to bring about coupling of the impeller with the outer runner, the said means connecting the inner runner with the casing comprising circumferentially spaced ribs to admit oil to the outer runner when the said ngers yield.

6. In a iluid coupling; a pair of runners each having a shell with partitions, said shells being concentric and substantially semi-circular in cross-section whereby they form substantially one-half of a toroidal cavity, an impeller comprising a shell with partitions and said shell forming the remainder of the toroidal cavity except for an outer annular portion, a casing surrounding said impeller and runners and having an inwardly projecting annular part extending into said portion and completing said toroidal cavity, ribs connecting said part with the inner of said runners, and yieldable deector means on the impeller normally deecting the oil pumped thereby into the inner runner and yieldable to permit the pumped oil to pass into the outer runner.

FREDERICK W. SEYBOLD.

REFERENCES CITED The following references are of record in the ille of this patent:

UNITED STATES PATENTS Number Name Date 2,061,997 Dunn Nov. 24, 1936 2,074,170 Dunn Mar. 16, 1937 2,284,123 Breer et a1 May 26, 1942 2,378,353 Zeicler June 12, 1945 2,428,134 Zeider Sept. 30, 1947 2,536,842 Dueld Jan. 2, 1951 

